High energy rate forming machine



Oct. 8, 1968 J. K. MUREK 3,404,555

HIGH ENERGY RATE FORMING MACHINE Filed Nov, 12, 1964 5 Sheets-Sheet 1 INVENTOR. JbSEF K All/EEK M a aom A r roe/v5 Y Oct. 8, 1968 Filed Nov. 12, 1964 HIGH J. K. MUREK 3,404,555

ENERGY RATE FORMING MACHINE 5 Sheets-Sheet 2 A r TOPM'EY Oct. 8, 1968 J. K. MUREK HIGH ENERGY RATE FORMING MACHINE 5 Sheets-Sheet 4' Filed Nov. 12, 1964 4 6 4 0 4 7 Q 6 K a fi M o fl a 6....) 0 9 4 9 2 9 I Z .fl 0 0 8 2 III 60 5 6 M @7 14. o m z 4 n m a H? mhwl! 1 J NW. m 6 fixg NM l 5 WK F F w 0 J 6 w 2 w 0 z a J 4 2 g g m 6 JFI' a IL 5 Al 6 w r, a M 2 h a F I 4 a0 AI I M Z I I: j w i-.. I 2 w/ I M I. I v. W. m 4 M A 'rra/evva Oct. 8, 1968 J. K. MUREK 3,404,555

HIGH ENERGY RATE FORMING MACHINE Filed Nov. 12, 1964 5 Sheets-Sheet 5 M0 FIG. 8 /62 W FIG. 7

INVENTOR. JZJEPA/ K MUPEK United States Patent 3,404,555 HIGH ENERGY RATE FORMING MACHINE Josef K. Murek, 4454 Casitas, San Diego, Calif. 92107 Continuation-in-part of application Ser. No. 334,473, Dec. 30, 1963. This application Nov. 12, 1964, Ser. No. 410,365

19 Claims. (Cl. 72-445) The present application is a continuation-in-part of application Ser. No. 334,473, filed on Dec. 30, 1963, now abandoned.

The present invention relates generally to high energy rate forming machine; more particularly, the invention relates to dynamic high rate forming machines adapted for repetitive cycling.

High energy rate forming machines, particularly those adapted for repetitive cycling operation, have been characterized by certain disadvantages and shortcomings. Primarily because of the high energy rates, high stresses and velocity to which components are subjected, problems of unreliability, maintenance and short service life have been general. These problems have been particularly difficult with respect to tensile impact loading and inability to isolate components from such loading and high rate stress. Efforts to relieve these problems have involved relatively complex and specialized structures and mechanisms. Repeat impacting of a ram against a workpiece after a forming impact has been a shortcoming which has resulted in damage to formed workpieces and additional stresses in machine components.

Relatively low efficiency has been a problem, this resulting in large part from loss during machine ,operation of input energy supplied as hydraulic pressure. Another problem has been inaccessibility and difficulty of replacing or repairing components, such as annular sealing elements utilized in the pressure chambers of certain machines. These and other disadvantages of prior machines are overcome or alleviated by machines according to the present invention.

It is therefore an object of the present invention to provide a novel high energy rate forming machine which provides improved ruggedness, reliability and service life.

An object of the invention is the provision of an improved high rate forming machine wherein components are effectively isolated from impact loading, and wherein tensile impact loading is substantially eliminated.

It is an object of the invention to provide a high rate forming machine according to the foregoing object wherein only the impacting ram and bolster are subjected to impact loading.

An object of this invention is the provision of a high energy rate forming machine wherein two energy sources simultaneously apply kinetic energy oppositely to a workpiece being formed.

An object of the present invention is to provide a machine according to the foregoing object wherein the respective energy sources are governable to equalize the opposite kinetic energies applied to the workpiece, thereby minimizing machine stresses and preventing repeat impact against the formed workpiece.

An object of this invention is to provide a high rate forming machine wherein decompression of compressed liquid provides high rate actuating energy.

An object of the invention is the provision of a high rate forming machine wherein greatly improved efiiciency is provided by utilizing compressed liquid to provide actuating energy.

An object of the present invention is to provide a high rate forming machine wherein substantially increased output energy capacity is provided by utilizing decompression of compressed liquid to provide actuating energy.

An object of the invention is the provision of a high energy rate forming machine wherein recocking of a ram is quickly and automatically effected without requiring any special system or component.

An object of this invention is to provide a high rate forming machine adapted for rapid and convenient maintenance and repair by the utilization of simplified components which are readily accessible.

An object of the invention is the provision of a high energy rate forming machine wherein a bolster and a ram are substantially equal in length to minimize or cancel impact shock waves.

Another object of this invention is: the provision of a high rate forming machine which provides a high degree of safety by incorporating features whereby the machine is actuable only intentionally.

Other objects, features and advantages of the present invention will become apparent to those versed in the art from a consideration of the following description, the appended claims and the accompanying drawings, wherein:

FIGURE 1 is a perspective view, partially in section, of a preferred embodiment of high energy rate forming machine according to the present invention;

FIGURE 2 is an elevational view largely in section, taken generally at line 2--2 in FIGURE 1, showing the machine components preparatory to actuation of the machine;

FIGURE 3 is a view similar to the view of FIGURE 2, showing the machine during the output strokes of its ram and bolster;

FIGURE 4 is a view similar to the views of FIGURES 2 and 3, showing the positions of machine components while the ram is moved to its secured or cocked position;

FIGURE 5 is an enlarged fragmentary sectional view of the structure encircled at 5 in FIGURE 3, showing details of a packing and sealing assembly about the ram;

FIGURE 6 is an enlarged fragmentary sectional view of the sealing and bearing structure encircled at 6 in FIGURE 2;

FIGURE 7 is a partial perspective view of the carriage assembly of the machine of FIGURES 1 through 4;

FIGURE 8 is a partial elevational sectional view, taken at the line 8--8 in FIGURE 9, showing a modified form of the machine of the invention wherein a frame supports the machine and the ram and bolster are slidably mounted by means of adjustable bearings; and

FIGURE 9 is a partial top view, partially in section, of the machine of FIGURE 8.

Referring to FIGURES 1 and 2 of the drawings, there is shown a preferred embodiment of the high energy rate forming machine of the present invention, which includes a head member,10 and a base plate 12 interconnected by four guide rods 14. The guide rods are secured to the base plate by appropriate flanges securing rings and bolts, as indicated at 16. The guide rods extend through openings in corner portions of the head member wherein shoulders (not shown) engage cooperating rod shoulders, and the head member is secured to the rods by nuts 18. A frame portion 20 of a carriage assembly, hereinafter described, is slidably mounted on the guide rods by means of appropriate openings in the corner portions of the frame. A bolster 22 is slida'bly mounted on the guide rods by means of sleeve bearings 24 in appropriate openings in its corner portions.

A base cylinder 26 is secured centrally on the base plate 12 by bolts in openings in its flange portion 28. Secured as by welding to enlarged portions of flange 26 at opposite sides of the base cylinder are two hydraulic fittings 28. Communicating with the respective fittings are electrically operated two-way valves 30, 32 which communicate with fluid couplings 34, and 36, respectively. A

hydraulic tube 38 is threadedly secured in each fitting 28 and extends vertically at each side of the machine, as shown.

The base cylinder 26 has a large cylindrical cavity or opening 40 which communicates with a source of hydraulic pressure (not shown) through a' passage 42 in the cylinder and an appropriate fluid coupling, for a purpose which is hereinafter described.

A reduced cylindrical section 44 of a positioning member 46 is in telescoping relation with base cylinder 26, and pressure sealing is provided between them by a packing assembly 48 (FIGURE 2). Positioning member section 44 and the base cylinder define an hydraulic pressure chamber 50, which serves as a locating pressure chamber and as an hydraulic actuating pressure chamber, as hereinafter described.

A large axial opening or cavity 52 is defined in positioning member 46 and communicates with a source of pressurized gas (not shown) through a passage 54 and an appropriate fluid coupling. Mounted in telescoping relation with the positioning member is a cylindrical chamber housing 56 having an axial cavity 58.

A bolster pressure chamber 60 is defined by the chamber housing 56, the positioning member 46 and their respective cavities or openings. Pressure sealing for the chamber is provided by an appropriate sealing assembly 62. The bolster 22 is positioned atop the chamber housing 56.

As shown in FIGURE 2, an ejector assembly is accommodated by a bore 64, a communicating reduced bore 66 in the bolster, and an axial recess in the chamber housing member 56. This assembly comprises a piston 68, a plunger 70 secured to the piston, a helical spring 72 about the plunger normally urging the piston downward, and a fitting 74 mounted in the lower opening of bore 66. The piston and plunger are actuated to drive an ejector rod 76 by hydraulic pressure applied through a passage 78 in the fitting 74, a passage 80 in housing member 56 and an appropriate fluid coupling.

As shown in FIGURES 2 and 3, a large cylindrical opening 82 having an end wall 84 is defined in each side portion of the bolster. Communicating with each opening 82 is a reduced bore 86 through which one of the hydraulic tubes 38 extends into the opening 82. Pressure sealing between each tube 38 and the bolster is provided by an annular packing assembly 88 which, as indicated, is adapted to provide pressure sealing in both directions.

The head member 10, secured at the upper ends of the guide rods as hereinbefore described, has an integrally formed pressure dome 90, a top opening 92 of which accommodates a fitting 94 of a fluid coupling for admission of pressurized gas.

A ram 96 is movable relative to the head member 10, and cooperates with the pressure dome to define an expansible ram pressure chamber 98. The ram comprises a lower rectilinear portion 100 and an upper cylindrical portion 102. Positive pressure sealing between the ram cylindrical portion 102 and the head member 10 is provided by the sealing assembly shown in FIGURE 5, which includes an annular fitting 104 in which is provided a passage 106 for admission of a quantity of oil 108 between the dome plate and the ram to provide sealing. Packing material 110 is secured between a gland 112 and a flange of fitting 104, and the packing gland and fitting are secured to the head member by bolts 114. A resilient sealing ring 116 in a recess in the head member provides pressure sealing between fitting 104 and the head member.

The ram 96 and the bolster 22 serve as tooling carriers. A die part 118 is secured by bolts to the lower surface of ram 96, and a second die part 120 is secured in confronting relation with die part 118 by appropriate bolts to the upper surface of the bolster 22. An axial passage in die part 120 accommodates the ejector rod 76. A workpiece 122 to be formed is positioned in die part 120.

Referring to FIGURES 1, 2 and 7, the carriage assembly includes the frame portion 20, gib portions 124, lower wall portion 126, a support portion extending upwardly from the lower wall and within the frame portion, and two downwardly extending cylindrical portions 130, all of which are integrally formed or cast together to provide rigidity and ruggedness. The integral carriage assembly is slidably mounted on the guide rods 14 by means of bores adjacent to each corner of frame portion 20.

Each of the four gib portions 124 has a bearing shoulder in which an appropriate bearing element is mounted for sliding engagement with the corners of rectilinear portion 100 of the ram 96. As shown, the ram is slidably mounted within the carriage assembly by means of the gibs 124.

The two cylindrical portions of the carriage assembly are in telescoping relation with the respective cylindrical bores 82 in the bolster. Each cylindrical portion 130 has a large axial opening having an end Wall 132 and cooperates with bore 82 to define an expansible holding pressure chamber 134. Pressure sealing between each cylindrical portion 130 and its cooperating bore is provided by a packing assembly 136 adapted to seal against fluid leakage in either direction.

A pivot bar 138 is mounted in and extends between openings in opposite side portions of frame portion 20, and pivotally mounted on each pivot bar 138 are two locking arms 140, on each of which is defined a locking shoulder 142. A second pivot bar 144 extends between Openings in the outer portions of each pair of locking arms 140, and secured as by welding to the pivot bar 144 is a piston rod 146 of a hydraulic actuator 148. A piston 150 of each actuator is secured to a rod 146 and separates pressure chambers 152 and 154 in the actuator. Chamber 152 communicates through an appropriate fluid coupling with a source of hydraulic pressure (not shown). The actuator has its housing secured as by welding to arms 156 which are integral with frame portion 20, thereby providing a unitary rigid assembly. A latch pivot bar 158 on each side of the ram is mounted in openings in opposite sides of the frame portion and in an opening in support portion 128. Mounted on each latch pivot bar 158 are two latch members 160, two on each side of the ram. At the side of each latch member adjacent to the ram is defined a generally rectangular latching shoulder 162, and on the opposite side of each latch member adjacent to a locking member is defined a locking shoulder 164.

The locking shoulder of each latch member 160 is adapted to engage the shoulder 142 of an adjacent locking member, when the cooperating locking and latch members are in the positions shown in FIGURE 2, wherein the surfaces of the mating shoulders 164 and 142 are tangential to a line from these shoulders to the center of the pivot bar 138.

Referring to FIGURE 2, limit switches are mounted adjacent to machine components and are electrically connected with the electrically operated valves 30, 32 to effect cycling of the valves during the cycle of operation of the machine. Two limit switches 166 are mounted at each side of the machine adjacent to the lower surfaces of locking arms 140, and are connected with the electrically operated valves 30, 32 by connectors 168. Similar limit switches 170 are mounted on the carriage frame adjacent to the upper surfaces of one of the locking arms on each side of the machine. Another limit switch 172 is mounted on a guide rod beneath the bolster 22 and is also electrically connected with the valves.

To prepare the machine for cycling operation, gas under appropriate pressure is introduced into the ram pressure chamber 98 through coupling 92, and gas under appropriate pressure is introduced into bolster pressure chamber 60 through passage 54 in positioning member 46. There is introduced into hydraulic pressure chamber hydraulic pressure sufiicient to support the positioning member 46, the chamber housing 56 and the bolster 22.

In the preferred mode of operation of the machine, the bolster actuating pressure system includes the chamber 50 as an hydraulic bolster actuating pressure chamber, in addition to the pneumatic bolster pressure chamber 60. In this mode of operation, the body of liquid in .chamber 50 is positively contained so that it is compressed with movement of the bolster assembly and positioning member 46; the chamber 50 is preferably larger than it appears in the drawings. The pressure utilized in the pneumatic bolster pressure chamber 60 to provide actuating energy is considerably less than when only that chamber is utilized to provide bolster actuating pressure. For example, in a machine having the proportions shown in the drawings, the pneumatic pressure in chamber 60 might be approximately one-half that utilized in the ram pressure chamber 98, in contrast with the utilization of substantially equal pressures in chamber 60 and ram pressure chamber 98 when chamber 50 does not serve as a source of bolster actuating energy.

It has been found that greatly improved efiiciency results from the utilization of chamber 60 as an hydraulic actuating pressure chamber. The improved efficiency results largely from the recovery of the energy of the hydraulic pressure introduced into expansible holding pressure chambers 134 to urge the bolster 22 and the carriage assembly apart. conventionally, approximately half of the energy input represented by hydraulic pressure 1s lost in machine operation. It has been found that efficiencies of over percent are obtainable by utilizing chamber 50 has an hydraulic actuating pressure chamber.

A cycle of operation commences with the introduction of hydraulic pressure into the expansible holding pressure chambers 134 to act upon the chamber end walls 84 and 132 to urge the bolster 22 and the carriage assembly apart. The bolster is thereby urged downward into its cocked position while compressing the gas in the bolster pressure chamber 60, and compressing the body of liquid in hydraulic actuating pressure chamber 50, in the preferred mode of operation. The holding pressure in the chambers 134 thus holds the bolster in this cocked position against the opposing force of the bolster actuating pressure system.

The action of the holding pressure urges the carriage assembly upward into the position shown in FIGURE 2, wherein the latch members 160 engage the ram and the locking arms 140 lock the latch members in place. The holding pressure exerts upward holding or latching force on the carriage assembly, with the ram in its cocked or secured position shown in FIGURE 2, the latch members 160 secure the ram by engagement of their latching shoulders 162 with marginal portions of the lower rectangular portion of the ram. Latch members 160 are secured in latching positions by the locking members 140, locking shoulders 142 of which engage the locking shoulders 164 of the latch members. Although this latching of the ram is mechanical and is independent of the actuators 148, relatively low pressure may be maintained in chambers 154 of the actuators to provide increased assurance against any possible accidental unlatching of the latch members 160.

Referring to FIGURE 3, an operating cycle is triggered by the introduction of hydraulic pressure into the chambers 152 of the actuators 148 to urge pistons 150 to exert rotative force at pivot bars 144 to rotate the locking members about pivot bars 138 to disengage locking shoulders 142 from. locking shoulders 164 of the four latch members 160, thereby freeing the latch members for pivotal movement about pivot bars 158.

Upon being thus unlatched and released, the ram 96 is suddenly impelled at high acceleration and velocity for an output stroke toward the bolster under the action of the ram pressure. The ram moves within the carriage assembly and is guided by the gibs 124.

Substantially simultaneously, the bolster 22 and chamber housing 56 are impelled for an output stroke under the action of the bolster actuating pressure system. Release of the ram and bolster is initiated by hydraulic pressure from an accumulator to chambers 52 to rotate lock members from their positions shown in FIG. 2 to their positions shown in FIG. 3. Limit switches 166 operate valve 32 to bleed the hydraulic fluid in holding pressure chambers 134 outwardly through tube 38, fittings 28 and couplings 34, 36 (FIG. 1), thus allowing the carriage system with lock members 140 to move downward relative to the bolster below the ram to engage lock members, as shown in FIG. 1, to recock the machine.

Upon the rapid release of the lock members 140 thus effected, the bolster, chamber housing 56 and the ram, are impelled towards each other at high acceleration and velocity under the action of the ram and bolster pressures to provide the output stroke. As stated, this system preferably includes hydraulic compression in chamber 50. Positioning member 46 is impelled with the bolster when this hydraulic compression is utilized.

The ram 96 and bolster 22 are thus impelled toward each other, as indicated by the arrows in FIGURE 3, and the workpiece 122 is formed by a high energy rate impact between the die parts 118 and 120.

Both the kinetic energy of the ram and the oppositely directed kinetic energy of the bolster and chamber housmg 56 are applied to theforkpiece. In the preferred mode of operation, utilizing hydraulic actuating pressure chamber 50, the kinetic energy of the positioning member 46 is also applied, and the kinetic energy applied to the workpiece includes a large proportion of the energy represented by the holding pressure introduced into the holding pressure chambers 134. As hereinbefore mentioned, the overall efliciency of the machine is thereby greatly increased. For example, the efiiciency has been found to be increased to over 80 percent.

A considerable part of the kinetic energy of the carriage assembly is also applied, the direction of the kinetic energy of the bolster impelling force being transmitted from the bolster to this assembly through the oil or liquid in chambers 134. The actuation of limit switches 166 by lock members 1 40, as they rotate from the positions shown in FIGURE 2 into the positions shown in FIG- URE 3, effects operation of the valves 32 to relieve the hydraulic holding pressure in holding pressure chambers 134 outwardly through tubes 38, fittings 28 and couplings 34, 36 (FIGURE 1). Upon impacting the workpiece and the ram, the bolster velocity suddenly drops, while the carriage assembly tends to move upward, thereby increasing the volume in expansible holding pressure chambers 134, thereby producing subatmospheric pressure, whereby the carriage assembly exerts .force and applies energy upwardly on the bolster. This action effectively increases the mass and kinetic energy of the bolster assembly, and additional kinetic energy is applied to the workpiece.

The rapid relieving of the holding pressure in chambers 134 effectively disconnects the carriage assembly from the bolster and from the ram during their output strokes, and the carriage assembly is freely movable on the tie rods 14. The carriage is isolated from rarn impact or shock by being mechanically disconected from the ram, and is isolated from bolster impact loading because the hydraulic holding pressure in chambers 134 drops to subatmospheric pressure, as hereinbefore mentioned.

In addition to operating valves 32 to relieve the holdin|g pressure, the actuation of limit switches 166 by the locking arms 140 simultaneously actuates a valve (not shown) to relieve pressure in chambers 152 of actuators 148, preparatory to the relatching of the ram by latch members 160.

After impact, the ram is moved into its cocked position and the gas in ram pressure chamber 98 is recompressed to re-establish the ram pressure, by the action of force applied by the bolster actuating pressure system. As indicated by the arrows and component positions in FIGURE 4, this force urges the chamber housing 56, the bolster 22 and the ram upward against the opposing weights and the pressure in the ram pressure chamber 98. The pressures in the bolster pressure chamber 60 and in hydraulic chamber after impact are predetermined to overcome the forces opposing this movement.

Upon the movement of the ram from its pre-latched position shown in FIGURE 4 into its cocked position shown in FIGURE 2, the four latch members 160 automatically pivot about pivot bars 158 under the action of gravity into their latching positions shown in FIGURE 2 wherein their latching shoulders 162 engage lower marginal portions of the ram. As will be understood from the geometric relations of the parts, the locking members move from their positions shown in FIGURE 4 into their locking positions shown in FIGURE 2, wherein they positively mechanically secure the latch members in their latching positions until the locking arms are positively moved by the actuators 148. The latching movement of the latch members 160 may be assisted by maintaining an appropriate pressure in chambers 154 of the actuators, although this is not essential. As previously mentioned, pressure in actuator chambers 152 is relieved prior to the movement of the ram into its cocked position by the actuation of limit switches 166 to operate an appropriate valve.

Movement of the locking arms into their locked positions shown in FIGURE 2 actuates a limit switch 170 adjacent to one of the locking arms to reverse the valves 32 to admit hydraulic pressure through the tubes 38 to reestablish the holding pressure in chambers 134. The holding pressure acts upon end walls 84 and 132 of the chambers to urge the carriage assembly and the bolster apart. The bolster is moved downwardly by the action of the holding pressure into its cocked position shown in FIGURE 2, while recompressing the gas in the bolster pressure chamber and in hydraulic chamber 50 to re-establish the bolster actuating pressure or pressures, preparatory to a repeat cycle of machine operation.

The holding pressure acts upwardly on the carriage assembly, thereby exerting holding force on the ram through latch members 160, although positive mechanical latching is provided without this holding force.

The ejector assembly may be operated to eject the formed part from the die part by the introduction of appropriate pressure through the passage 80 in chamber housing 56 to urge the ejector piston 68 and plunger 70 upward to urge the ejector rod through the axial passage 122 in the die member to eject the formed part.

A cycle of operation of the machine is thus completed, and a new cycle is commenced with the introduction of pressure into the chambers 152 of the actuators 148 to effect unlatching movement of the latch members from the ram, as hereinbefore described.

The relieving of the holding pressure in chambers 134 would be effected without utilizing limit switches 166 to operate the valves 32 to relieve the pressure, or in the event of failure of the limit switches or valves to function. An alternate mode of operation or safety feature is thereby provided. The automatic relieving of the holding pressure results from the increase in the volume of the holding pressure chambers 134 upon initial movement of the carriage assembly with the bolster under the action of the pressure in bolster chamber 60, as the ram is released for its output stroke. The volumes of chambers 134 increase because the hydraulic tubes 38 are fixed while cylindrical carriage portions 130 move upward. The hydraulic pressure in the chamber suddenly drops, for example from 3,000 p.s.i. to subatmospheric pressure. If this mode of operation is intended, the limit switch 172 adjacent to the lower surface of the bolster is operated by movement of the bolster into its cocked position to close the valves 32 to retain the hydraulic holding pressure in the chambers 134 prior to the latching of the ram.

The forming machine is capable of operation with the bolster 22 remaining stationary. In this mode of operation, the bolster pressure chamber 60 is not pressurized. The machine is utilized as a drop-hammer, and the ram being im-pelled in the manner hereinbefore described toward the stationary bolster 22. To provide a shock absorbing feature, gas can be introduced with hydraulic fluid into the pressure chamber 50. This mode of operation facilitates the forming of successive sections of elongated members. Prior high rate machines, wherein the bolsters move upward during the ram stroke, cannot properly accommodate such forming of elongated members, because the moving bolster disturbs the position of the elongated member relative to the die, with resultant deformation of the member and/or failure to form the member in the desired configuration.

FIGURES 8 and 9 illustrate a modified form of the invention wherein different means are utilized for slidably mounting the carriage and bolster. This embodiment is otherwise generally similar in structure and in operation to the previous embodiment.

A frame disposed about the machine comprises an upper section 174 extending across the top of the machine, a central section 176 at each side, and a lower section 178, all secured together by four tie rods 180 and nuts 182. The frame is supported at each side by an I-bearn 184, and the base cylinder 26 rests upon a lower plate of the lower frame section 178.

A modified carriage frame 186 has at each corner a vertical bearing surface 188 inclined :relative to the machine axis. A modified bolster 190 has at each corner a similar vertical and inclined bearing surface 192.

Hydraulic fittings 194, like fittings 30 of the previous embodiment, are supported by horizontal plates of central frame sections 176, and extending from the fittings into the bolster are hydraulic tubes 196, which are similar to the longer hydraulic tubes 38 of the previous embodiment.

Two bearing assemblies are mounted on each central frame section 176, each assembly extending along a bearing surface 188 of carriage 186 and .a bearing surface 192 of the bolster 190 below. A vertical elongated mounting bar 198 of each bearing assembly extends along the carriage and the bolster, and is secured as by welding in a corner defined by plates of the central frame section 176. An .adjustment member 200 is mounted on the bar 198 adjacent to each bolster bearing surface 192 and has a plurality of spaced inclined portions 202. Attached to the mounting member 200 by screws (not shown) is a bolster bearing 204 which has a bearing surface oriented to engage the bolster bearing surface 192, and which has a plurality of spaced inclined portions 206 engageable with portions 202 of the adjustment member to provide for positional adjustment of the hearing relative to the bolster.

Attached to each bar 198 adjacent to bearing surface 188 of the carriage is an adjustment member 208, similar to ad ustment member 200 and having similar spaced inclined portions (not shown). Secured as by screws to the member 208 is a carriage bearing 210 which has a surface oriented to engage the carriage surface 188. Spaced inclined portions (not shown) are provided on bearings 210 for positional adjustment of the bearing relative to the carriage bearing surface 188.

In the operation of the machine, the carriage bearings 210 and the bolster bearings 204 serve to slidably mount the carnage assembly and the bolster for their respective movements, thus serving the function of the guide rods 14 in the embodiment previously described.

Certain of the features and advantages of machines according to the invention are hereinafter mentioned. The utilization of chamber 50 as an hydraulic actuatmg pressure chamber for the bolster, wherein a body of contained liquid is compressed and decompressed to provide actuating energy, provides greatly improved efficiency by applying to a workpiece energy put into the machine in the form of holding pressure introduced into chambers 134. Such energy is conventionally lost in the operation of machines. Further, such utilization of the chamber 50 provides increased acceleration of the bolster assembly, because of the relatively very rapid decompression and expansion of a compressed liquid.

From the foregoing description and from the drawings, it will be understood that the only machine components which are subjected to impact loading are the ram and the bolster, which must necessarily be subject to such loading and stress. The impact loading of these members is compressive, and no component is subjected to tensile impact loading. The carriage assembly being disconnected from theram and from the bolster during the output strokes of these members and during impact, is not subjected to impact loading or high stress.

The integral and rugged construction of the carriage assembly facilitates positive latching and unlatching action by the latching or securing components relative to the carriage assembly on which they are mounted.

The ram and bolster being substantially equal in length, impact shock waves in these members travel the same distance and meet at substantially the same time. They therefore tend to be minimized or canceled. The ram and bolster are both relatively long in relation to their width, and deflection or deformation are therefore substantially preeluded.

The machine herein described provides a high degree of safety, because the ram is positively locked or secured mechanically, without requiring any fluid pressure for this purpose, until the latching mechanism is positively and intentionally operated to effect release.

High rate forming machines according to the invention incorporate structural and operational features which provide an important advantage in preventing bounce or repeat impact 'upon a formed workpiece after the forming impact. Such bounce subjects machine components to additional impact loading and stress and damages formed parts. The aforementioned action of the bolster pressure immediately after impact in moving the bolster and ram to effect movement of the ram to its cocked position tends to prevent bounce by urging the components together. The equal lengths of the ram and bolster tend to prevent bounce by minimizing or canceling the impact shock waves.

The equalizing or matching of the respective kinetic energies applied oppositely by the ram and the bolster constitutes an important capability and feature of machines according to the invention. It is probably the most important factor in preventing the aforementioned bounce or repeat impact upon a formed workpiece. The equalizing or matching of the opposite kinetic energies results in their being substantially absorbed upon the impacting of the workpiece. To achieve equalizing of the opposite kinetic energies, corelation is effected among the ram and bolster actuating pressures, the areas upon which the respective pressures act, and the respective masses impelled by the respective pressures. The calculation of the kinetic energies of the oppositely moving masses may be calculated in terms of the respective volumes of the ram and pressure chambers, the initial gas pressures in these chambers, and adiabatic gas expansion, so that after the adiabatic gas expansion there is an equalizing of the kinetic energy of the ram with the kinetic energy actually trans ferred to the workpiece from the mass impelled by the bolster pressure. In the case of the machine herein described, the corelation and calculations must take into consideration the kinetic energy which is applied by the of the interconnection through the subatmosp-heric pressure in the holding pressure chambers.

Although specific embodiments of the present invention have been illustrated and described herein, it will be understood that the same are merely exemplary of presently preferred embodiments capable of attaining the objects and advantages hereinbefore mentioned, and that the invention is not limited thereto; variations will be readily apparent to those versed in the art, and the invention is entitled to the broadest interpretation within the terms of the appended claims.

The inventor claims:

1. A high energy rate forming machine comprising a ram, means cooperating with the ram to define an expansible ram pressure chamber, means for releasably securing the ram in cocked position, said securing means including latch means engageable with the ram and means for actuating the latch means to release the ram for an output stroke energized by the ram pressure, bolster means mounted for movement toward the ram, bolster actuating pressure means comprising an expansible pressure chamber, means for releasably holding the bolster in cocked position and for rapidly releasing the bolster means in response to said actuation of the latch means simultaneously with said releasing of the ram for a bolster output stroke toward the ram energized by the bolster actuating pressure means, whereby the ram and the bolster means are impelled toward each other to impact an object therebetween, means for returning the ram to its cocked position and re-establishing the ram pressure in the ram pressure chamber, and means for returning the bolster means to its cocked position and re-establishing the actuating pressure in the bolster actuating pressure means.

2. A high rate forming machine according to claim 1 wherein the bloster actuating pressure means includes an hydraulic actuating pressure chamber wherein a body of liquid is compressed by movement of the bolster means into its cocked position to provide actuating energy.

3. A high energy rate forming machine comprising a ram, means cooperating with the ram to define an expansible ram pressure chamber, means for releasably securing and for rapidly releasing the ram for an output stroke energized by the ram pressure, bolster means confronting and mounted for movement relative to the ram, bolster actuating pressure means comprising an expansible pressure chamber, means for holding in cocked position and for rapidly releasing the bolster .means substantially simultaneously with said releasing of the ram for a bloster output stroke toward the ram energized by the bolster actuating pressure means, whereby the ram and the bolster means are impelled toward each other to impact an object therebetween, said ram and bolster after impact being urged by the bolster actuating pressure means in the direction of said bolster output stroke to move the ram into its cocked position and re-establish the ram pressure, the force of the bolster actuating pressure means after impact being predetermined to overcome the forces opposing such movement, and means for returning the bolster to its said cocked position.

4. A high energy rate forming machine comprising a ram, means cooperating with the ram to define an expansible ram pressure chamber, means for releasably securing and for rapidly releasing the ram for. an output stroke energized by the ram pressure, bolster means confronting and mounted for movement relative to the ram, bolster actuating pressure means including means cooperating with the bolster means to define an expansible pneumatic bolster pressure chamber, said bolster actuating pressure means also including an hydraulic actuating pressure chamber wherein a body of liquid is compressed when the bolster means is in cocked position, and means for holding in cocked position and for rapidly releasing the bolster means substantially simultaneously with said releasing of the ram for a bolster output stroke toward the ram energized by the bolster actuating pressure means, whereby the ram and the bolster means are impelled toward each other to impact an object there between.

5. A high rate forming machine according to claim 4, wherein said hydraulic actuating pressure chamber is defined by means including a base member, and wherein said hydraulic actuating pressure chamber serves also as a locating pressure chamber into which liquid under a locating pressure is introduced to selectively position the bolster to govern the spacing between the ram and the bolster and to reduce shock transmission to a foundation.

6. A high energy rate forming machine comprising a ram, means cooperating with the ram to define an expansible ram pressure chamber, means for releasably securing and for rapidly releasing the ram for an output stroke energized by the ram pressure, bolster means confronting and mounted for movement relative to the ram, means cooperating with the bolster means to define an expansible bolster pressure chamber, means for holding in cocked position and for rapidly releasing the bolster means substantially simultaneously with said releasing of the ram for a bolster output stroke toward the ram energized by the bolster pressure, whereby the ram and the bolster means are impelled toward each other to impact an object therebetween, means including a base member defining an expansible locating pressure chamber, and means establishing a locating pressure in the locating pressure chamber to selectively position the bolster to govern the spacing between the ram and the bolster and to reduce shock transmission to a foundation.

7. A high energy rate forming machine comprising a ram, means cooperating with the ram to define and expansible ram pressure chamber, means for releasably securing and for rapidly releasing the ram for an output stroke energized by the ram pressure, bolster means confronting and mounted for movement toward the ram, bolster actuating pressure means comprising an expansible pressure chamber, said ram securing means and the bolster means cooperating to define at least one ex-pansible holding pressure chamber, means for introducing pressure into the holding pressure chamber to urge the bolster and said ram securing means apart to position the ram securing means for securing the ram and to urge the bolster into and releasably hold it in its cocked position, and means for releasably securing and rapidly releasing the ram for an output stroke energized by the ram pressure and for releasing the bolster means substantially simultaneously for a bolster output stroke toward the ram energized by the bolster actuating pressure means, whereby the ram and the bolster means are impelled toward each other to impact an object therebetween.

8. A high energy rate forming machine comprising a ram, means cooperating with the ram to define an expansible ram pressure chamber, bolster means mounted for movement toward the ram, bolster actuating pressure means comprising an expansible pressure chamber, said ram securing means and the bolster means cooperating to define at least one expansible holding pressure chamber, means for introducing pressure into the holding pressure chamber to urge the bolster and the ram securing means apart, whereby the ram securing means is positioned for securing the ram and whereby the bolster is urged into and held in its cocked position to establish the bolster pressure in the bolster pressure chamber, means for releasably securing in cocked position and rapidly releasing the ram for an output stroke energized by the ram pressure and for rapidly releasing the bolster means substantially simultaneously with said releasing of the ram for a bolster output stroke toward the ram energized by the bolster pressure, whereby the ram and the bolster means are impelled toward each other to impact an object therebetween, said ram and bolster after impact being urged by the bolster actuating pressure means in the direction of said bolster output stroke to move the ram into its cocked position and reestablish the ram pressure, the force of the bolster actuating pressure means after impact being predetermined to overcome the forces opposing such movement, and means for returning the bolster to its said cocked position.

9. A high energy rate forming machine comprising a ram, means cooperating with the ram to define an expansible ram pressure chamber, means for releasably securing and for rapidly releasing the ram for an output stroke energized by the ram pressure, bolster means confronting and mounted for movement relative to the ram, bolster actuating pressure means comprising an expansible pressure chamber, and means for holding and for rapidly releasing the bolster means substantially simultaneously with said releasing of the ram for a bolster output stroke toward the ram energized by the bolster pressure, whereby the ram and the bolster means are impelled toward each other to impact an object therebetween, said bolster actuating pressure means and the ram pressure and the respective masses impelled thereby being corelated to substantially equalize the opposite respective kinetic energies applied by said masses upon impacting said object, whereby the kinetic energies are absorbed by the object, said ram and bolster after impact being urged by the bolster actuating pressure means in the direction of said bolster output stroke to move th ram into its cocked position and re-establish the ram pressure, the force of the bolster actuating pressure means after impact being predetermined to overcome the forces opposing such movement, and means for returning the bolster to said cocked position.

10. A high energy rate forming machine comprising a ram, means cooperating with the ram to define an expansible ram pressure chamber, carriage means mounted for movement relative to the ram, gib means on the carriage engaging the ram, means on the carriage for releasably securing and rapidly releasing the ram, said securing means having latch means adapted to engage the ram, having means for locking the latch means in engagement with the ram and having actuator means for operating the latch means, thereby releasing the ram for an output stroke energized by the ram pressure, means for disconnecting the carriage from the ram while the gib means guides the ram during its output stroke to isolate the carriage from impact loading, bolster means confronting and mounted for movement relative to the ram, bolster actuating pressure means comprising an expansible pressure chamber, and means for holding and for rapidly releasing the bolster means substantially simultaneously with said releasing of the ram for a bolster output stroke toward the ram energized by the bolster actuating pressure means, whereby the ram and the bolster means are impelled toward each other to impact an object therebetween.

11. A high energy rate forming machine according to claim 10 wherein the latch means comprise a plurality of latch members mounted on the carriage and spaced about the ram, each of said latch members being adapted to engage a marginal portion of the ram, the locking means comprise a plurality of locking arms, each of said arms being mounted on the carriage adjacent to a respective one of the latch members and being adapted to engage the latch member and secure it in engagement with the ram, and the actuator means comprise fluid pressure actuators secured to the carriage and connected with the locking arms to disengage the locking arms from the latch members.

12. A high energy rate forming machine comprising a ram, means cooperating with the rain to define an expansible ram pressure chamber, carriage means mounted for movement relative to the ram, gib means on the carriage and engaging the ram, latch means pivotally mounted on the carriage and having a first shoulder adapted to engage the ram, locking means pivotally mounted on the carriage and having a shoulder engageable with a second shoulder of the latch means to secure 13 the latch means in engagement with the ram, actuator means on the carriage for operating the locking means to disengage said locking means shoulder from the latch means second shoulder, thereby releasing the ram for an output stroke energized by the ram pressure, means for disconnecting the carriage from the ram while the gib means guides the ram during its output stroke to isolate the carriage from impact loading, bolster means confronting and mounted for movement relative to the ram, bolster actuating pressure means comprising an expansible pressure chamber, and means for holding and for rapidly releasing the bolster means substantially simultaneously with said releasing of the ram for a bolster output stroke toward the ram energized by the bolster actuating pressure means, whereby the ram and the bolster means are impelled toward each other to impact an object therebetween.

13. A high energy rate forming machine comprising a ram, means cooperating with the ram to define an expansible ram pressure chamber, carriage means mounted for movement relative to the ram, gib means on the carriage engaging the ram, means on the carriage for releasably securing and rapidly releasing the ram, said securing means having latch means adapted to engage the ram, having means for locking the latch means in engagement with th ram and having actuator means for operating the latch means, thereby releasing the ram for an output stroke energized by the ram pressure, bolster means mounted for movement toward the ram, bolster actuating pressure means comprising an expansible pressure chamher, said ram securing means and the bolster means cooperating to define at least one expansible holding pressure chamber, means for introducing pressure into the holding pressure chamber to urge the bolster and the ram securing means apart, whereby the ram securing means is positioned for securing the ram and whereby the bolster is urged into and held in its cocked position to establish pressur in the bolster actuating pressure means, and means for rapidly relieving the holding pressure to release the bolster means substantially simultaneously with said releasing of the ram for a bolster output stroke toward the ram energized by the bolster actuating pressure means, whereby the ram and the bolster means are impelled toward each other to impact an object therebetween, said rapid relieving of the holding pressure effectively disconnecting the carriage means and gib means to isolate them from impact loading, said ram and bolster after impact being urged by pressure in the bolster pressure chamber in the direction of said bolster output stroke to move the ram into its cocked position and reestablish the ram pressure, the force of the bolster actuating pressure means after impact being predetermined to overcome the forces opposing such movement, and means for returning the bolster to its said cocked position.

14. A high energy rate forming machine according to claim 13, wherein said ram pressure and bolster actuating pressure means and the respective masses impelled thereby are corelated to substantially equalize the opposite respective kinetic energies applied by said, masses upon impacting said object.

15. A high rate forming machine according to claim 13, wherein the bolster actuating pressure means includes an hydraulic actuating pressure chamber wherein a body of liquid is compressed when the bolster means are in cocked position to provide bolster actuating energy.

16. A high energy rate forming machine comprising a ram, means cooperating with the ram to define an expansible ram pressure chamber, carriage means mounted for movement relative to the ram, gib means on the carriage engaging the ram, means on the carriage for releasably securing and rapidly releasing the ram, said securing means having latch means adapted to engage the ram, having means for locking the latch means in engagement with the ram and having actuator means for operating the latch means, thereby releasing the ram for an output stroke energized :by the ram pressure, means for disconnecting the carriage from the ram while the gib means guides the ram during its output stroke to isolate the carriage from impact loading, bolster means confronting and mounted for movement relative to the ram, bolster actuating pressure means comprising an expansible pressure chamber, and means for holding and for rapidly releasing the bolster means substantially simultaneously with said releasing of the ram for a bolster output stroke toward the ram energized by the bolster actuating pressure means, whereby the ram and the bolster means are impelled toward each other to impact an object therebetween, said bolster and ram pressures and the respective masses impelled thereby being corelated to substantially equalize the opposite respective kinetic energies applied by said masses upon impacting said object, whereby the kinetic energies are absorbed by the object.

17. A high energy rate, forming machine comprising a ram, means cooperating with the ram to define an expansible ram pressure chamber, carriage means mounted for movement relative to the ram, gib means on the carriage engaging the ram, means on the carriage for releasably securing and rapidly releasing the ram, said securing means having latch means adapted to engage the ram, having means for locking the latch means in engagement with the ram and having actuator means for operating the latch means, thereby releasing the ram for an output stroke energized by the ram pressure, means for disconmeeting the carriage from the ram while the gib means guides the ram during its output stroke to isolate the carriage from impact loading, bolster means confronting and mounted for movement relative to the ram, bolster actuating pressure means comprising an expansible pressure chamber, and means for holding and for rapidly releasing the bolster means substantially simultaneously with said releasing of the ram for a bolster output stroke toward the ram energized by the bolster pressure, whereby the ram and the bolster means are impelled toward each other to impact an object therebetween, said ram and bolster after impact being urged by force of the bolster actuating pressure means in the direction of said bolster output stroke to move the ram into its cocked position and re-establish the ram pressure, the force of the bolster actuating pressure means after impact being predetermined to overcome the forces opposing such movement.

'18. A high energy rate forming machine according to claim 17 wherein said bolster and ram pressures and the respective masses impelled thereby being corelated to substantially equalize the opposite respective kinetic energies applied by said masses upon impacting said object, whereby the kinetic energies are absorbed by the object.

19. A high energy rate forming machine comprising a ram carrying a die part, means cooperating with the ram to define an expensible ram pressure chamber, carriage means mounted for movement relative to the ram, gib means on the carriage engaging the ram, means on the carriage for releasably securing and rapidly releasing the ram, said securing means having latch means adapted to engage the ram, having means for locking the latch means in engagement with the ram and having actuator means for operating the latch means, thereby releasing the ram for an output stroke guided by the gib means and energized by the ram pressure, bolster means mounted for movement toward the ram and carrying a die part, bolster actuating pressure means comprising an expansible pressure chamber, at least one cylinder means on the carriage, at least one cylinder means on the bolster confronting and in telescoping relation with said carriage cylinder means to define an expansible holding pressure chamber, means for introducing pressure into the holding pressure chamber to urge the bolster and the ram securing means apart, whereby the carriage means is positioned for engagement of the ram by said securing means and whereby the bolster is urged and held in its cocked position to compress the bolster actuating pressure means to provide actuating energy, and means whereby operation of said latch means releases the bolster means substantially simultaneously with said releasing of the ram for a bolster output stroke toward the ram energized by the bolster actuating pressure means are impelled toward each other to impact an object therebetween, said rapid relieving of the holding pressure effectively disconnecting the carriage means and gib means to isolate from them from impact loading, and means for returning the ram to its cocked position.

v References Cited UNITED STATES PATENTS FOREIGN PATENTS 6/1954 Germany.

CHARLES W. LA=NHAM, Primary Examiner.

15 G. P. CROSBY, Assistant Examiner. 

1. A HIGH ENERGY RATE FORMING MACHINE COMPRISING A RAM, MEANS COOPERATING WITH THE RAM TO DEFINE AN EXPANSIBLE RAM PRESSURE CHAMBER, MEANS FOR RELEASABLY SECURING THE RAM IS COCKED POSITION, SAID SECURING MEANS INCLUDING LATCH MEANS ENGAGEABLE WITH THE RAM AND MEANS FOR ACTUATING THE LATCH MEANS TO RELEASE THE RAM FOR AN OUTPUT STROKE ENERGIZED BY THE RAM PRESSURE, BOLSTER MEANS MOUNTED FOR MOVEMENT TOWARD THE RAM, BOLSTER MEANS PRESSURE MEANS COMPRISING AN EXPANSIBLE PRESSURE CHAMBER, MEANS FOR RELEASABLY HOLDING THE BOLSTER IN COCKED POSITION AND FOR RAPIDLY RELEASING THE BOLSTER MEANS IN RESPONSE TO SAID ACTUATION OF THE LATCH MEANS SIMULTANEOUSLY WITH SAID RELEASING OF THE RAM FOR A BOLSTER OUTPUT STROKE TOWARD THE RAM ENERGIZED BY THE BOLSTER ACTUATING PRESSURE MEANS, WHEREBY THE RAM AND THE BOLSTER MEANS ARE IMPELLED TOWARD EACH OTHER TO IMPACT AN OBJECT THEREBETWEEN, MEANS FOR RETURING THE RAM TO ITS COCKED POSITION AND RE-ESTABLISHING THE RAM PRESSURE IN THE RAM PRESSUR CHAMBER, AND MEANS FOR RETURNING THE BOLSTER MEANS TO ITS COCKED POSITION AND RE-ESTABLISHING THE ACTUATING PRESSURE IN THE BOLSTER ACTUATING PRESSURE MEANS. 